Seal lubrication for rotary engines



April 12, 1966 M. EEEEE LE 3,245,386

Fi l e d 0 c t 2 9 l 9 62 INVENTOR. M AX EJEN T E LE ATTDR April 12.,1966 M. 'BENTELE SEAL LUBRICATION FOR ROTARY ENGINES Filed Oct. 29, 19624 Sheets-Sheet 2 INVENIOR. MAX E:E NTELE %mzw w. /(med ATTEIRNEY A ril12, 1966 1NVENTR MAX E1ENTELE April 12, 1966 M. BENTELE SEALLUBRICAAIION FOR ROTARY ENGINES Filed Oct. 29, 1962 4 Sheets-Sheet 4.

1NVENTOR. MA X EE NTE LE wm /r jj ATTURNEY United States Patent O3,245,386 SEAL LUBRICATION FOR ROTARY ENGINES Max Bentele, Ridgwood,NJ., assignor to Curtiss Wright Corporation, a corporation of DelawareFiled Oct. 29, 1962, Ser. No. 233,561 3 Claims. (Cl. 1238) The presentinvention relates broadly to the art of rotary mechanisms and isparticularly directed to lubrication means for the sealing means forsuch rotary mecha nisms.

The invention is particularly useful in connection With rotarymechanisms similar to that disclosed in United States Patent Number2,988,065, although as will become apparent, this invention is notlimited to this specific type of rotary mechanism. In the followingdescription the invention is described in relation to an internalcombustion engine, but the invention is also suitable for fluid pumpsand fluid motors.

A rotary engine as disclosed in said patent comprises an outer body orhousing having a cavity therein and an inner body or rotor disposedtherein rotatable relative to the outer body, about an axis laterallyspaced from, but parallel to the axis of said cavity. The inner body isjournaled on an eccentric portion of a shaft which is coaxial with theouter body and journaled in bearings carried by the outer body endWalls. The outer body has axially-spaced end walls and a peripheral wallinterconnecting the end walls to form said cavity; the inner surface ofthe cavity peripheral wall having a multilobed profile which ispreferably basically an epitrochoid. The inner body or rotor has endfaces disposed adjacent to said outer body end Walls for sealingcooperatin therewith, and has a peripheral surface with a plurality ofcircumferentiallyspad apex portions, each carrying a radiallymovahleseal or seal means for sealing engagement With the multilobed innersurface of the outer body peripheral wall to form a plurality of workingchambers between the two bodies which vary in volume upou relativerotation of thetwo bodies. Each apex seal of the inner body runsaxially, separating the adjacent working chambers, and is receivedWithin an outwardly-facing groove running axially from one end face tothe other of the inner body at its associated apex portion on the innerbody. During rotation of the inner body, the apex seal means slidecontinuously along With their outer edges in bearing against the innersurface of the peripheral wall.

In certain prior Otto-type combustion engines the combustion chamberseal lubrication has been effected by mixing oil in the engine fuel.This, however, is not always desirable. This method causes high oilconsumption because a large part of the oil is burned or exhaustedbefore reaching the apex seal and inner surface.

In the past, in an attempt to avoid mixing oil to the fuel, it has beenproposed for both Otto-type and dieseltype engines to supply metered oilto the apex seal through the rotor. Such oil supply through the rotor issubject to relatively higher rotor temperatures and therefore coking ofthe oil in the rotor oil passages may occur. Mechanisms in the rotor,including their valves and springs, are also subject -to high andvariable acceleration forces so that it is diflcult to design such amechanism, which can operate elfectively. In addition, since each apexportion requires its own separate mechanism, control of the oil becomesa complex problem.

An object of the present invention comprises the provision of a rotarycombustion engine in which a novel lubricating means for the apex sealsis provided to improve seal lubrication and withopt excessive use of thelubricating medium.

Specifically, instead of mixing oil to the fuel or pumping oil throughthe rotor and out through the grooves of the apex seals, this inventionproVi des passage means With valve means which is disposed in thehousing and preferably in its peripheral wall, and which automaticallysupplies oil to a port in the peripheral-wall innersurface inintermittent releases, timed by the valve means to occur once for eachrotor apex passing the oil port.

Thus, relatively cool oil is supplied directly to the apex seal engagingsurfaces requiring lubrication, such as between the inner surface of theperipheral wall and outer edges of the apex seals and also between theside faces of the apex seals and their adjacent groove walls, and isreleased in a timed and etficient manner so that the oil is not burnedor exhausted befor e reaching these surfaces. Further, the lubncatingoil supply is regulated to the engine speed, and this als o reduces oilwastage particularly under varying speeds.

Another object of the invention is to furnish a multiple-sensing valvemeans which is simultaneously regulated by the gas pressures in theworking chambers as well as by the rotor speed, thereby regulating thequantities of oil released in proportion -to the engine load as well asregulating the flow of the oil supply in accordance with the enginespeed so that oil consumption is controlled in accordance With engineloads and speeds.

Still another object is to furnish an apex-seal lubricat ing means whichis operated and controlled by the apex seal itself.

A further object is to furnish an apex-seal lubricat ing means which isoperated and controlled by varying chamber gas pressure occuringadjacent to one region of the inner surface of the housing of the rotarymechamsm.

A Still further object is to furnish an apex-seal lubricat ing devicehaving flow control means With no moving parts.

An additional object is to fumish rotonseal lubricating means which canbe au integral part of a stationary housing wall of the rotarymechanism.

Still another object is to fumish a novel integral pump and meteringarrangement located near the point of oil injection.

Other objects of the invention will become apparent upon reading theanexed detail description in connection With the drawings in which:

FIG. 1 is a diagrammafic transverse view of a rotary engine embodyingthe invention;

FIG. 2 is an enlarged view of circled portion A of FIG. 1;

FIG. 3 is a view similar to FIG. 2 showing another embodiment of theinvention; L

FIG. 4 is a view similar to FIG. 2 showing Still another embodiment;

FIG. 5 is a sectional view taken along lime 55 on FIG. 4;

FIG. 6 is a view similar to FIG. 2 showing a further embodiment;

FIG. 7 is a sectional view taken along lime 77 of FIG. 6;

FIG. 8 is a view similar to FIG. 2 showing a similar embodiment with amodified passage means;

FIG. 9 is a sectional view taken along line 99 of FIG. 8.

Referring to the drawings, the housing or outer body of a rotarycombustion engine comprises spaced end walls 10 and 12, as shown in FIG.9, and a peripheral walll4 as shown in FIG. 1 disposed between andinterconnecting said end walls to form a cavity therebetween. The innersurface of the outer body comprises the inner surface 16 of theperipheral wall 14 and the inner faces of the end walls 10 and 12.

The inner surface 16 of the peripheral wall 14 preferably has amultilobed profile in cross-section which preferably is basically anepitrochoid.

Inside and eccentric to the housing is disposed an inner body or rotorhaving a plurality of circumferentiallyspaced apex portions 20 about itsouter periphery. A shaft 22, having an axis 24, which is coaxial withthe axis of the outer-body cavity and along which the end Walls and 12are spaced, extends through the outer body and is journaled in bearings(not shown) carried by the'end Walls 10 and 12. The shaft 22 has aneccentric portion 26 on which an inner body or rotor 18 is journaled,the axis of the inner body 18 and the eccentric 26 being indicated at28.

Each of said apex portions has radially-movable apex seal means 32received Within a single outwardlyfacing groove extending in a directionparallel to the rotor axis from one end face to the other of the rotor18 and urged radially outward by spring means 33 into sealing engagementwith the peripheral wall inner surface. The inner body 18 also has endfaces having end-face seals means 34 and intermediate seal elements 36disposed in sealing engagement with the end Walls 10 and 12 whichtogether with the apex seals 32 forms a plurality of work ing chambers38 which vary in volume upon rotation of the inner body 18 relative tothe stationary outer body.

During rotation of the inner body 18, the apex seal means 32 slidecontinuously along with their contact edges in bearing against the innersurface 16 of the peripheral wall 14, and the intermediate seal elements36 and end face seal strips 34 slide continuously along the fiat innersurfaces et the end walls 10 and 12. In order to maintain the relativemotion of the inner body 18 relative to the stationary outer body aninternal gear (not shown) is secured to the inner body coaxially withthe inner body axis 28 and is disposed in mesh with a fixed gear (notshown) secured to the outer body coaxial with the outer body axis 24.

The outer body has intake port means 40 for supply of an intake chargeto the working chambers 38 and has exhaust port means 42 for dischargeof exhaust gases from the engine. If needed, a suitable spark plug 44may be provided to ignite the intake charge.

The engine so far described is substantially similar to the enginedisclosed in the aforementioned United States Patent Number 2,988,065and for additional description reference is made to said patent. Theseal arrangement so far described is substantially similar to the sealarrangement disclosed in United States Patent Number 3,033,180 andreference is made to said patent for further description of said sealmeans.

In FIG. 1, the apex-seal lubricating means 45 is shown as an integralpart assembled in the outer body where it does not require specialsupporting structure and where it is not subject to rotor vibration andacceleration forces.

Three diflerent forms of apex-seal lubricating means are illustrated inFIGS. 2, 3 and 6. In FIG. 2, the outer body has a cylindrical member 46threaded into a bore 48 in its peripheral wall 14 at the bottom of whichis a recess 50 which functions as a small storage space or reservoir forlubricating oil. The cylindrical member 46 has a coaxial oil-supplypassage 52 connected to an oil supply source (not shown) for fee dingoil into therecess 50. The oil-supply passage 52 has a check valve 54disposed where it enters into the recess 50, which admits oil to therecess 50 through a passage 55 passing through the check valve 54 whenthe pressure therein drops below a predetermined value. The outer bodyalso has flow-control means with discharge passage means 56 extendingfrom the recess 50 through the peripheralwall inner surface forintermittently controlling the flow of lubricating oil from the recess50 through the oil-discharge passage means 56 in order to lubricate theinner surface 16 and the apex seals 32.

In FIG. 2, the oil fiowcontrol means comprises a valve member 58 havinga flange or head portion 64 to overlie and close the passage 56 and toopen the passage when the valve head 64 is raised or lifted. The valve58 also has an inwardly extending actuating stem portion 60 disposedWithin a bore 62 in the peripheral wall and projecting inwardly beyondthe peripheral-wall inner surface 16, such that the valve member 58 islifted or raised by an apex seal 32 against a spring 66 to open theoil-discharge passage 56 each time au apex seal 32 passes across thevalve member. Thus, the valve member is opened a number of times in eachrevolution of the rotor equal to the number of rotor apex seals 32 orportions 20, whereby intermittent oil releases are automaticallysupplied to the apex seal means 32 by this mechanically-actuated valve58. The actuating portion 60 of the valve member 58 of this embodimentprotrudes radially inside the periph eral-wall inner surface 16 when itis in a closed position. This mechanicaltype valve member 58 releasesoil to the inner surface in front of the apex seal 32 as the actuatingportion 60 is lifted upon contact with each passing apex seal 32, andeach quantity of oil released to the oildischarge passage 56 andinjected into the chamber 38 is proportional to the outward forceexerted thereon by each apex seal 32. When the actuating portion 60fully protrudes, the valve member 58 is fully closed; and when theactuating portion 60 is lifted so that it is flush with the innersurface 16, the valve 58 is then fully open; and when partly lifted andpartly protruding, the valve 58 is partly open. After each discharge ofoil from the recess 50 the valve 58 closes as the apex seal moves offits protruding end and the check valve 54 opens in response to thepressure diferential of the oil in supply passage 52 and the pressure inthe recess 50 t0 refill the recess 50.

The apex-seal strips are urged in a radially outward direction not onlyby the spring means 33 but also by the force of the gas pressure in theadjacent working chamber having the higher pressure. This latter gaspressure acts radially outwardly under each apex seal. Thus, themagnitude of the radially outward force on each apex seal means 32increases with increase in engine load and therefore the magnitude ofthe lift of the valve 58 by each apex seal means likewise varies withload. Hence, oil flow is governed by both engine speed and load, andregulated by a valve member 58, which is operated by the action of theapex seal 32 itself. Also, at constant speed, oil injection varies withengine load; while at constant load, oil injection varies with enginespeed.

At any substantial load of the apex seal against the protrudingactuating portion, the valve member is lifted fully and the apex sealremains in contact with the peripheral wall so that there is no gasleakage between chambers. At light load, the valve is only partly liftedand the apex seal is not flush with the peripheral-wall inner surface sothat although some leakage can then occur across the apex seal, this isnot detrimental at light loads.

The amount of oil injected each time the valve 58 is raised obviously isproportional to the magnitude of the lift of the actuating portion 60.Since the recess 50 is full of oil upon injection, the actual volume ofoil injected for each valve actuation depends primarily on the volumedisplaced by the plunger or stem as it lifts.

In FIG. 2, the spring means 66 is disposed between the check valve 54and valve member 58 to urge them apart toward their closed positions.The spring means 66 is designed and calibrated te suit the variableapexseal radial force so that the valve member 58 properly opens, and tosuit the oil pressure in the oilsupply passage 52 which is maintained sothat the check valve 54 opens when the pressure difierential across thecheck valve reaches a predetermined value. The type of spring 66 used isnot critical, and other types are suitable for idling and noloadconditions. In addition, oil drip or drainage from the recess 50 to theperipheralwall inner surface 16 is minimized at shut-down. Ihus, if anapex seal 32 should stop opposite the actuating portion 60, only some ofthe oil in the recess 50 wonld drain, or by suitable design of the valvespring 66 the pressure of the apex-seal 32 at shutdown would not liftthe actuating portion 60 to permit oil drainage.

The preferred location for the embodiment of the apex-seal lubricatingmeans 45 in FIG. 2 With a mechanical-type valve 58 in a conventionalair-throtded engine, that is, an Ottotype engine having a variablethrottle valve in the engine air intake, is in the cold lobe of theinner surface 16 in the region between the intake port 40 and spark plug44 and upon or just beyond, in the direction of rotor rotation, one endof the major axis of the multilobe profile of the inner surface 16. Forexample, the valve 58 preferably is located at such region A in FIG. 1so that oil is applied to the apex-seal 32 before it moves into thecombustion region that is be- -fore the apex-seal reaches the region ofboth the highest gas pressure and temperature, and heaviest friction andWear. This preferred location is Within the chamber 38 during its intakephase. At this location in a conventional air-throttled engine, the gaspressure of the work ing chamber varies in proportion to the engineload.

However, in an engine having no variable throttle valve in the engineair intake, as in a diesel, the pressure in the working chambers as theymove through the region A would not vary With load. Hence, in such anunthrottled engine, the preferred location of the apexseal lubricatingmeans 45 is in a more downstream -region indicated at Al in FIG. 1.'Ihis region A'1 extends. from a point on the peripheral wall at whichthe trail ing apex-seal of a working chamber is located when combustionis initiated therein to a point at which this apex-seal is located whensaid working chamber is in its top -dead center position where theapex-seal lubricating means 45 is not subjected to the maximum gaspressures and temperatures which ocur after the top dead center positionof a working chamber.

Another location, indicated at region B in FIG. 1, which is suitable asan alternate location for the lubricating means 45 with the valve 58 inboth a throttled and unthrottled engine is in the hot lobe prior to theexhaust port 42 and upon or near the major axis as indicated at region Bin FIG. 1, where the chamber gas pressure likewise varies in proportionto the engine load.

Sti ll another location, indicated at region C in FIG. 1, which issuitable as an alternate location for the valve 58 in both a throttledand unthrottled engine is at the minor axis or waist portion of theinner surface profile between the exhaust port 42 and the intake port40, but =at this location, illustrated at position C in FIG. 1, thenecessary variation of gas pressure with engine load is not aspronounced as at the locations A, Al and B in FIG. 1.

In FIG. 3, another embodiment of the apex-seal lubricating means 45a isshown which is similar to that in FIG. 2. For case of understanding, theparts of FIG. 3 corresponding to the parts of FIGS. 1 and 2 have beendesignated by the same reference numerals but With a subscript a addedthereto. The chief difrerence is that its actuating portion 60a is flushwith the inner surface 16:: when in a closed position instead ofprotruding. Here, the apex-seal 32a is not required to lift theactuating portion 60a. The actuating portion 60a is al-ways clear of thepassing apex-seal strips 32a, and is lifted solely -by gas pressurepressing on its end face. The actuating portion 60a is flush With theperipheral-wall inner surface 16a when the valve member 5811 is in aclosed position, and when the actuating portion 60a is li fted or pushedradially outward by the working chamber gas pressure upon its and face,the valve member 58a is opened. Due to the increase in the oil pressurein the. recess 50a and the simultaneous opening of the passage 56acaused by the lifting of the actuating portion 60a and flange 64a et thevalve member 58a, a quantity of oil is released which is proportional tothe, radial gas, pressure force on the valve actuating stem 60a, so thatthe quantity of oil injected to the inner surface 1611 is alsoproportional to both engine speed and load.

After each discharge of oil from the recess 50a the valve 58a closes andwhen the pressure in the adjacent working chamber 38a drops suflicientlythe check valve 54a opens in response to the pressure differential Ofthe oil in supply passage 52a and the pressure in the recess 50a torefill the recess 50a.

In both embodiments shown in FIGS. 2 and 3, the quantity of oil-released is regulated by the gas pressure in the working chamber, thatis, indirectly in the mechani. cal-type valve member 58 in FIG. 2 anddirectly in the gas-piston valve member 58a in FIG. 3. The preferredlocation and *best alternate locations wonld therefore be the same forboth embodiments, and these locations, which depend on the type ofengine throttle, were described previously.

In FIG. 3 as in FIG. 2 a common spring 66a urges both valves 54a and 58ain a closing direction. In addition, in FIG. 3 a separate spring 67 isprovided to urge the valve 58a in a closing direction. In this way thespring 66a can be made quite light.

The head 64a of the valve member 58a in FIG. 3, as in FIG. 2, opens andcloses the oil discharge passage 56a as the valve 58a rises and returns,the head having a downwardly extending peripheral flange for seating.This head has an annular groove or recess 65 between the valve stem andthe fiange on the side of its discharge passage 56a and communicatingwith the passage 56a when the valve is closed. With this grooveconstruction on the last portion of the return stroke of the valve 58a.some of the oil trapped in the groove will be forced through the oilpassage 56a because of the resistanoe to backfiow around the outer edgeof the valve head or flange 64a, thus providing a second, lesser oilinjection.

FIG. 4 shows an embodiment of an apex-seal lubricating means 451)similar to FIG. 3, except having a passage 56!) which is cut in thesurface of the stem-like actuating portion 6%. For case ofunderstanding, the parts of FIGS. 4 and 5 corresponding to the parts ofFIGS. 1 and 2 have been designated by the same reference numerals butwith a subscript b added thereto.

In FIG. 4, the oil discharge passage 56b is formed by a singlelongitudinal groove in the stem outer surface disposed adjacent to itswall bore or opening 62]). Also, the springs 66b and 671) in thisembodiment are illustrated as leaftype instead of coil type. Both thepassage 56b and springs 66b and 67!) are also usable in the firstembodirnent in FIG. 2, as well as in the second embodiment in FIGS. 3and 4. The use of a separate spring 6717 against the check valve 5415and a separate spring 66b against the valve member 58]) permits casierspring design and calibration.

FIG. 6 shows still another embodiment -of the apex seal lubricatingmeans 45c. For case of understanding, the parts of FIGS. 6 and 7corresponding to the parts of FIGS. 1 and 2 have been designated by thesame reference numerals but with a subscript c added thereto.

The apex-seal lubricating means 45c in FIG. 6 includes an oil-dischargepassage means 56c extending from the recess 50c through theperipheral-wal] inner surface 16C. However, instead of having a valvemember with an actuating portion like the valve member 58 of FIG. 2, ithas a second, gas-passage means 68 which separately extends from therecess 50c through the peripheralwall inner surface 16c and iscircumferentially spaced a sufficient distance from the first,oildischarge passage means 56e, so that when an apex seal moves underthe apex-seal lubricating means it is momentarily disposed between thedischarge ends of the passages 56c and 68. In additien, the apex-seallubricating means 450 is disposed at 3. position in the outer bodyperipheral wall 166 such that when an apex is disposed between thedischarge ends of its passages 560 and 68 the pressure in the workingchamber on one side of the apex seal e.g. the passage 68 side issubstantially greater than the pressure in the working chamber on theother side of the apex seal. Accordingly, each time an apex strip 32cpasses between the two passage openings 560 and 68 the higher gaspressure in the working chamber communicating with the passage 68 iseffective through this passage t force the oil out of the recess 500 andthrough the oil-discharge passage 560 and into the lower-pressurechamber. The quantity of oil injected is proportional to the gaspressurediflerential, which in turn is substantially proportional to the engineload when properly located as described hercafter. Hence, oil fiow isagain governed by both engine speed and load, and regulated by a simpleflow-control means with no moving parts.

In FIG. 6, as in the other embodiments, the check valve 54c opens whenthe pressure difierential across the valve 540 is above a predeterminedamount. After oil has been discharged from the recess 500 and an apexseal has moved bey0nd both passages 56c and 68 both passages Willcommunicate with the same working chamber. When the pressure in thislatter chamber drops below the oil supply pressure in the passage S2cits check valve 54c will open to admit oil into the recess 50e. Thus,when the gas pressure in the emptied recess 500 becomes lower than theoil-supply pressure and the check valve 54c opens, oil flows into therecess 50L to refill the recess. The passages 56c and 68 aresufliciently small and offer suflicent resistance to oil flowtherethrough that When the recess 50c becomes filled with oil, thepressure in the recess is substantially the same as the oil supplypressure whereupon the spring 660 closes the check valve 546. The oilremains in the recess 500 outil au apex seal again moves between itsdischarge passages 56c and 68 whereupon the difierential between the twopassages again forces oil from the recess 50c through the passage 56cfor lubrication of the peripheral-wall inner surface and apex seals.

The preferred location on the inner surface l6c for thedifierential-pressure type of apex seal lubricating means 45c in FIG. 6is similar to the preferred locations indicated for the other twoembodiments in FIGS. 2 and 3. When used in a throttle engine, thepreferred location is at region A as illustrated in FIG. 1, that is, inthe cold lobe of the inner surface 160 in the region between the intakeport 40 and spark plug 44 preferably somewhat beyond the adjacent end ofthe major axis of the multilobe profile of the inner surface 160. Whenused in an unthrottled engine, the preferred location is at region A1 inFIG. 1, which is, as illustrated, located downstream from region A inFIG. 1. At these locations, the oil is injected behind the apex sealstrip 32c and is picked up by the succeeding apex seal strip since thechamber gas pressure is higher on the leading side than the trailingside of the apex seal strip 32C. Also, the lubrication is therebyapplied just before the seal strip 320 is subject to the highestpressure, friction and wear during compression and combustion. The bestalternate location for the mechanism of FIG. 6 in both throttled andunthrottled engines is at the other end of the major axis of themultilobe profile 160, in the hot lobe region shown at region B inFIG. 1. In the region B, the pressure in the working chamber on thetrailing side of an apex seal is higher than on the other side.Therefore, when the apex seal lubrication mechanism is located in theregion B the oil is injected from recess 500 ahead of the apex sealstrip 32e. Also, pressure, friction and wear on the seal strip 32cthereafter in the exhaust region is not as severe and therefore lesslubrication of the apex seal is required than inthe region followinglocation A.

In FIGS. 8 and 9, the mechanical-type of apex-seal lubricating means 45dpreviously described and shown in FIG. 2 has oil passage means 560.including a distribution passage 70 connected to a plurality ofdischarge openings 72 through the peripheral-wall inner surface 16a,which is a feature applicable to all embodiments in FIGS. 2 through 7.For ease of understanding the parts of FIGS. 8 and 9 corresponding tothe parts of FIGS. 1 and 2 have been designated by the same referencenumerals but with a subscript d added thereto. The discharge openings 72are preferably spaced axially-parallel for distributing oil evenly alongthe apex seal length for improved lubrication.

The apex seal lubricating means preferably is installed in theperipheral wall 14 as illustrated in FIGS. 2 through 9. Instead however,said apex seal lubrication means may be installed in the end walls 10and 12. The peripheral wall location is preferred because themechanicaltype valve (FIG. 2) has an actuating portion 60 with its endedge protruding inside the outerbody inner surface 16 forming a ramp,and the rounded outer edge of the apex seal 32 slides over the ramp moreeasily than the squared end-edges of the apex seal 32 and intermediateseal member 36. The dilerential-pressure type of apex seal lubricatingmechanism (FIG. 6) has two passages 68 and 56c extending from the recess50c to the inner surface 16c and spaced apart a distance to allow onepassage to be on each side of the apex seal 32e, and since the apex seal32c is much thinner than the intermediate seal element 36 the smalldiameter passages are shorter and are less likely to coke or clog. Thegas- .pressure type of valve as shown in FIG. 3 (and also as shown inFIG. 4) oprates equally well when disposed in either the peripheral wall14a or end walls 10 and 12, but since it is primarily desired tolubricate the outer edge of the apex seal 32a, the most convenientlocation of the oil-discharge opening 56a and valve member 58a isadjacent to the apex-seal outer ed-ge in the peripheral wall 14a. Thelubricating oil from the openings 72 (FIG. 9) adjacent to the end walls10 and 12 can also lubricate the adjacent intermediate seal members. Ifan apex seal lubricating mechanism is disposed in the end wall 10 or 12,it is preferably located radially outwardly of the path of the end faceseals 34 and preferably in the path of the intermediate seal members 36for their dubrication, and the preferred peripheral location is adjacentto its preferred location in the peripheral wall described previously.

The various improvements of the invention provide improved apex-seallubrication during engine operation; prevent wasting of the oil; avoidmixing oil to the fuel; avoid metering devices connected to the enginedrive; avoid clogging and coking of oil-supply passages; avoidacceleration and vibration forces of the rotor; provide oil injection tothe seals automatically, efficiently and in a timed fashion; provide anintegral pump and meter arrangement near the point of injection; andregulate oil injection in accordance with both engine speed and engineload.

While I have described my invention in detail in its present preferredembodiment it will be obvious to those skilled in the art afterunderstanding my invention that various changes and modifications may bemade therein without departing from the principle or scope thereof. Itis intended by the appended claims to cover all such modifications.

What is claimed is:

1. A rotary mechanism comprising in combination an outer body havingaxially spaced end walls and a periphera;l wall interconnecting said endwalls to define a cavity in said outer body; an inner body disposedwithin said outer body for rotation relative to said outer body, saidinner body having axially spaced end faces in sealing engagement withsaid end walls and a plurality of circumferentially spaced apex portionsin sealing engagement with the inner surface of said peripheral wall,said inner body defining with said outer body a plurality of workingchambers Which vary in volume on relative rotation of said bodies withcyclical variation between higher and lower pressures in each of saidworking chambers during rotation; said outer body having an oilreservoir and oil discharge passage means communicafing between saidreservoir and said working chambers and a piston bore communicatingbetween said reservoir and said working chambers; a resiliently loadedreciprocable piston disposed within said bore and having at one end aworking face exposed to said chambers; said piston having at the otherend a valve plate disposed within said reservoir and normally closingsaid oi1 discharge passage from said reservoir; said valve plate havingon the side facing said oil discharge passage an annular recess incommunication With said passage when said valve is closed; said pistonand valve plate being responsve to said relative rotation and to saidhigher pressure portion of said cycle to open said discharge passage tosaid reservoir and to displace oil from said reservoir to provide afirst discharge through said passage of said displaced cil, said pistonand valve plate being further responsive to said relative rotation andto said lower pressure portion of said cycle to close said passage fromsaid reservoir and to provide a second discharge through said passage ofoil from said recess.

2. The combination of claim 1, wherein said reservoir has a supplyconduit and check valve means disposed therein to prevent back fiowthrough said conduit during oil displacement from said reservoir.

3. The combination of claim 1, wherein the working face of said pistonin closed position is substantially flush with the inner surface of saidperipheral wall.

References Cited by the Examiner UNITED STATES PATENTS 952,707 3/ 1910Maximilan 92156 X 1,321,340 11/1919 Stoke 230207 1,347,959 7/ 1920McGann 92-156 X 2,289,441 7/1942 LeValley 230152 2,540,714 2/1951 Curtiset a] 230-207 2,780,406 2/1957 Feldbush 230207 2,824,687 2/ 1958Osterkamp 230207 3,106,197 10/1963 Mallory 239-87 X 3,174,466 3/1965Scherenberg.

FOREIGN PATENTS 742,876 1/ 1933 France.

SAMUEL LEVINE, Przmury Examiner.

JOSEPH H. BRANSON, JR., Examiner.

1. A ROTARY MECHANISM COMPRISING IN COMBINATION AN OUTER BODY HAVINGAXIALLY SPACED END WALLS AND A PERIPHERAL WALL INTERCONNECTING SAID ENDWALLS TO DEFINE A CAVITY IN SAID OUTER BODY; AN INNER BODY DISPOSEDWITHIN SAID OUTER BODY FOR ROTATION RELATIVE TO SAID OUTER BODY, SAIDINNER BODY HAVING AXIALLY SPACED END FACES IN SEALING ENGAGEMENT WITHSAID END WALLS AND A PLURALITY OF CIRCUMFERENTIALLY SPACED APEX PORTIONSIN SEALING ENGAGEMENT WITH THE INNER SURFACE OF SAID PERIPHERAL WALL,SAID INNER BOBY DEFINING WITH SAID OUTER BODY A PLURALITY OF WORKINGCHAMBERS WHICH VARY IN VOLUME ON RELATIVE ROTATION OF SAID BODIES WITHCYCLICAL VARIATION BETWEEN HIGHER AND LOWER PRESSURES IN EACH OF SAIDWORKING CHAMBERS DURING ROTATION; SAID OUTER BODY HAVING AN OILRESERVOIR SAID OIL DISCHARGE PASSAGE MEANS COMMUNICATING BETWEEN SAIDRESERVOIR AND SAID WORKING CHAMBERS AND A PISTON BORE COMMUNICATINGBETWEEN SAID RESERVOIR AND SAID WORKING CHAMBERS; A RESILIENTLY LOADEDRECIPROCABLE PISTON DISPOSED WITHIN SAID BORE AND HAVING AT ONE END AWORKING FACE EXPOSED TO SAID CHAMBERS; SAID PISTON HAVING AT THE OTHEREND A VALVE PLATE DISPOSED WITHIN SAID RESERVOIR AND NORMALLY CLOSINGSAID OIL DISCHARGE PASSAGE FROM SAID RESERVOIR; SAID VALVE PLATE HAVINGON THE SIDE FACING SAID OIL DISCHARGE PASSAGE AN ANNULAR RECESS INCOMMUNICATION WITH SAID PASSAGE WHEN SAID VALVE IS CLOSED; SAID PISTONAND VALVE PLATE BEING RESPONSIVE TO SAID RELATIVE ROTATION AND TO SAIDHIGHER PRESSURE PORTION OF SAID CYCLE TO OPEN SAID DISCHARGE PASSAGE TOSAID RESERVOIR AND TO DISPLACE OIL FROM SAID RESERVOIR TO PROVIDE AFIRST DISCHARGE THROUGH SAID PASSAGE OF SAID DISPLACED OIL, SAID PISTONAND VALVE PLATE BEING FURTHER RESPONSIVE TO SAID RELATIVE ROTATION ANDTO SAID LOWER PRESSURE PORTION OF SAID CYCLE TO CLOSE SAID PASSAGE FROMSAID RESERVOIR AND TO PROVIDE A SECOND DISCHARGE THROUGH SAID PASSAGE OFOIL FROM SAID RECESS.